Windrow merger

ABSTRACT

A windrow merger includes at least one conveyor for transporting material picked up by at least one pickup head member, the at least one pickup head member having a plurality of spaced apart spacers disposed along a length dimension of the at least one pickup head member, and an internal drive assembly disposed within a longitudinal aperture defined internal to the plurality of spaced apart spacers, the drive assembly for imparting a rotational motion to a plurality of tines. A method of forming the windrow merger is further included.

RELATED APPLICATION

This application is a division of application Ser. No. 13/075,766 filedMar. 30, 2011, which is hereby fully incorporated herein by reference.

TECHNICAL FIELD

The present invention relates to a farm implement. More particularly,the present invention relates to a device for merging one or morewindrows in a field.

BACKGROUND OF THE INVENTION

When a feed product, such as alfalfa, is ready to be harvested, theproduct may be cut and then raked into long, generally parallel windrowsin the field. In cases in which the product is too moist for furtherprocessing, the product is typically left in such windrows to afforddrying of the product by the wind and sun in the field. After severaldays of drying in the field, the windrow is typically picked up and theproduct may be either stored or further processed, such as by bailing.

In order to minimize the number of windrows that must be picked up, itmakes economic sense to merge one or more of the windrows into a singlelarger windrow. Such merging minimizes the number of passes through thefield that are necessary to pick up the crop. Accordingly, there is aneed in the industry for ever more efficient windrow mergers. Typically,a merger may have three individual pick up heads positioned adjacent oneanother when in the working disposition. Each pick-up head is typicallypowered by an individual hydraulic motor. In the past, the hydraulicmotor was positioned at an end of the pick-up head. In such disposition,the hydraulic motor prevented adjacent pick-up heads from being disposedproximate each other. Accordingly, there was a significant gap betweenthe conveyors of each of the adjacent pick-up heads and crop beingtransported on the conveyor was lost through the gap.

Additionally, in the past, the tines of the pick-up head were driven ata constant rotational speed. Accordingly, the crop that had been pickedup was transported at a constant speed to be deposited unevenly and atthe forward edge of the conveyor.

Further, prior art mergers were susceptible to a bouncing action inducedin the two outboard pick-up heads as a result of passage over a roughfield surface. Such bouncing caused the pick-up heads to miss picking upcrop that was laying the field. Additionally, it would be desirable tobe able to provide a bias to the outboard pick-up head merging thepick-up heads to stay in contact with the underlying ground. As an aidto this, it would be desirable to have a selectable adjustable height ofthe pick-up heads relative to the underlying ground.

Finally, it may be desirable to offset the windrow merger with respectto the towing tractor such that an outboard pick-up head would followdirectly behind the tractor and the center pick-up head and the secondoutboard pick-up head would be displaced laterally with respect to thedirect of travel of the tractor.

SUMMARY OF THE INVENTION

The windrow merger of the present invention substantially meets theaforementioned needs of the industry. The individual pick-up heads ofthe windrow merger are driven by an internally disposed hydraulic motor.Such disposition eliminates the need for a hydraulic motor disposed onan end of an individual pick-up head. Accordingly, the individualpick-up heads can be disposed very close to one another when in theworking disposition. The gap existing between adjacent conveyors isminimized to the point that crop being transferred from a conveyor to anadjacent conveyor experiences virtually no loss in making the transitionbetween the adjacent conveyors.

An additional feature of the windrow merger of the present invention iscam driven tines. The effect of the cam is to accelerate the tangentialrotational speed of the tines proximate the apex of tine motion. Theeffect of the acceleration of the tines is to accelerate the speed ofthe crop being carried by the tines such that the crop does not merelydrop onto the leading edge of the conveyor but is effectively spread outacross the full width dimension of the conveyor by means of a flickingmotion imparted to the crop by the accelerated tines.

A further feature of the instant windrow merger is a respectivehydraulic accumulator that is hydraulically in communication with arespective actuator that is coupled to an individual outboard pick-uphead. The effect of the hydraulic accumulator is pressurized upon upwardmotion of the outboard pick-up head. After passing the rise in theground, the accumulator transfers such hydraulic pressure back to theactuator to extend the actuator, thereby exerting a downward bias on theindividual outboard pick-up heads in order to minimize bounce of theindividual outboard pick-up head over uneven underlying ground.

A further feature of the windrow merger of the present invention isindividually adjustable height of the individual pickup heads above theground and of the merger itself. To accomplish this, the skids that aredisposed beneath the individual pick-up heads are mounted to the frameof the respective pick-up head by means of a shiftable mount.Preferably, the shiftable mount is comprised of a pair of actuators thatcan set the distance between the skid and the pick-up head frame asdesired to effect varying heights of the respective pick-up head abovethe underlying ground. Additionally, the truck assembly is shiftablerelative to the remainder of the chassis member such that the chassismember may be positioned at a selected height above the underlyingground.

A further feature of the windrow merger of the present invention is thatthe wheels on the truck assembly are steerable. By such steering, it ispossible to offset the track of the windrow merger as compared to thetowing tractor in order to displace the windrow merger either right orleft with respect to the direction of travel of the towing tractor.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a front quarter perspective view of the windrow merger of thepresent invention;

FIG. 2 is a rear quarter perspective view of the windrow merger;

FIG. 3 is a rear quarter perspective view of the windrow merger;

FIG. 4 is a perspective view of a pick-up head;

FIG. 4 a is a cut-away view of the portion of the pick-up head of FIG. 4as depicted in the rectangle 4 a;

FIG. 5 is a side elevational view of a cam;

FIG. 6 is a side rear perspective view of the lower structure of theright side of the windrow merger;

FIG. 7 is a perspective of the windrow merger in the transportdisposition;

FIG. 8 is a perspective view of the windrow merger with a pick-up headin the first transitional disposition and a pick-up head in the foldedtransport disposition;

FIG. 9 is a perspective view with an outboard pick-up head in theworking disposition and a second outboard working head in the firsttransitional disposition; and

FIG. 10 is a top planform view of the windrow merger in a transitiondisposition between the transport disposition and the workingdisposition.

DETAILED DESCRIPTION OF THE DRAWINGS

The windrow merger of the present invention is shown generally at 10 inthe figures. Merger 10 includes two major components, chassis member 12and pick-up head members 14, 16, and 18.

The chassis member 12 of the merger 10 includes four majorsubcomponents; mount assembly 20, tongue assembly 22, support assembly24, and truck assembly 26.

Turning first to the mount assembly 20, as depicted in FIG. 1, anarched, boxed frame 30 includes a pair of forward directed couplers 32for removably coupling to a tractor or other towing vehicle. A PTO shaft34 is operably coupled at a first end to a gear box 36. The PTO shaft 34may be coupled at its second end to the PTO of a tractor. The gear box36 is preferably disposed in the arch defined by the frame 30 and iscoupled to a hydraulic pump 38. Preferably, the gear box 36 is usefulfor either stepping up or reducing the rpm available at the PTO shaft ofthe tractor. A shackle 40 is fixedly coupled to the rear of the archedframe 30. The shackle 40 includes a pair of spaced apart shacklebrackets 42. Each of the shackle brackets 42 has a bore 44 definedtherein, the bores 44 being in registry. A pin 46 may be received withinthe two bores 44.

The tongue assembly 22 of the chassis member 12 includes at its proximalend a receiver 50. The receiver 50 is sized such that the receiver 50may be disposed in the aperture defined between the shackle brackets 42.The pin 46 may be received within a bore (not shown) defined with thereceiver 50 for pivotally coupling the tongue assembly 22 to the mountassembly 20.

The receiver 50 is fixedly coupled to a boxed tongue 52. The boxedtongue 52 preferably rises at an angle and then extends rearward in agenerally horizontal disposition to overlie the pick-up head member 18.As depicted in FIG. 2, a removable support 53 may be disposed beneaththe boxed tongue 52 to support the forward portion of the merger 10 whenthe merger 10 is not connected to a tractor or the like.

A plurality of hard hydraulic lines 54 are disposed on the upwarddirected surface of the tongue 52. At their proximal ends, the hydrauliclines 54 are coupled by flexible hydraulic lines 55 (see FIG. 2) thatare coupled to the hydraulic pump 38. At their distal ends, the hardhydraulic lines 54 are coupled by flexible hydraulic lines (not shown,but that are similar to the flexible hydraulic lines 55) to the variousactuators that are described below.

The distal end of the boxed tongue 52, terminates in a flange 56. Aboxed member 58 is disposed rearward of the distal end of the tongue 52.The boxed member 58 includes a flange 60 which is mated to the flange 56by a plurality of bolts disposed in bores defined in the respectiveflanges 56, 60. Structure 64 depends from the boxed member 58. A rearcover 66 and a pair of essentially mirror image side covers 68 arecoupled to the depending structure 64. The depending structure 64, therear cover 66 and the two side covers 68 comprise components of thesupport assembly 24.

The support assembly 24 includes a generally triangular shaped fixedstructure 70. The apex of this triangular shape depends from the boxedmember 58. It should be noted that passing a vertical plane through thelongitudinal axis of the tongue 52 as depicted in FIG. 1 splits themerger 10 into two mirror image halves, the components described belowbeing replicated on both sides of the plane.

The fixed structure 70 of the depending structure 64 includes at leastin part a support beam 72. The support beam 72 is affixed to a basesupport 74. The base support 74 includes a pair of outward directed andspaced apart brackets 76. See also FIG. 10. Each of the brackets 76 hasa bore (not shown) defined therein and a pin 80 disposed in the boresdefined in the respective brackets 76. The pin 80 extends from bracket76 to bracket 76. The pin 80 pivotally couples a head support 78 to thebase support 74. The head support 78 is pivotable about the pin 80, theaxis of rotation being the longitudinal axis of the pin 80 which isessentially a fore-aft axis.

A translation actuator 82 operably couples the head support 78 to arespective one of the pick-up head members 14, 16. See also FIG. 6. Thetranslation actuator 82 has a cylinder end coupling 84 that is pivotallycoupled to the head support 78. The translation actuator 82 further hasa piston end coupling 86 that is pivotally coupled to a respectivepick-up head member 14, 16 by means of a generally vertically disposedpin 87 disposed in a coupler 85.

A further actuator is coupled to the head support 78. This actuator isthe lift actuator 88. The lift actuator 88 has a cylinder end coupling90 that is pivotally coupled to the support assembly 24 by means of thefixed structure 70 proximate the apex thereof. Such coupling is by meansof a bracket 92, the bracket 92 having a pin 93 therein. A piston endcoupling 94 of the lift actuator 88 is pivotally coupled to the headsupport 78 by means of a bracket 96, the bracket 96 having a pin 95disposed in a pair of bores (not shown) defined in the bracket 96.

A hydraulic accumulator 97 is preferably affixed to the support beam 72.The hydraulic accumulator 97 is fluidly coupled to the lift actuator 88by flexible hydraulic lines not shown, but similar to lines 55 notedabove. A remotely controllable valve 98 is affixed to the hydraulicaccumulator 97. The valve 98 is shiftable between a disposition in whichthe hydraulic accumulator 97 is fluidly coupled to the lift actuator 88and a disposition in which the hydraulic accumulator 97 is fluidlyisolated from the lift actuator 88.

The truck assembly 26 is the fourth assembly of the chassis member 12and is rotatably coupled to the fixed structure 70 by means of a pair ofspaced apart pins 103, a pair of adjustable links 107, and a pair ofactuators 116, described in greater detail below.

Accordingly in order to affect the above noted coupling, as depicted inFIG. 8, a pair of truck brackets 100 are fixedly coupled to thestructure 70. The truck brackets 100 are pivotally coupled to a coupler102 affixed to an axle plate 112 by means of the pin 103. A pair of linkbrackets 104 are fixedly coupled to the structure 70. Each of the linkbrackets 104 is pivotally coupled to a respective adjustable link 107 bymeans of a pin 106. See FIG. 3. The final means of coupling the truckassembly 26 to the structure 70 are the actuators 116. Accordingly, apair of actuator brackets 100 are fixedly coupled to the structure 70.Each of the respective actuator brackets 108 are pivotally coupled to anactuator 116 by means of a pin 110.

The fourth assembly of the chassis member 12 is the truck assembly 26.The truck assembly 26 generally is disposed rearward of the chassismember 12 is operably pivotally coupled to the support assembly 24 asnoted above. The truck assembly 26, best viewed in FIGS. 1-3, includesan axle plate 112 and a wheel assembly 113. The axle plate 112 istransversely mounted with respect to the longitudinal axis of the merger10. The upper surface of the axle plate 112 includes a pair of upwarddirected spaced apart actuator brackets 114. Each of the actuators 116has a piston and coupler 118 that is coupled to the bracket 114 by meansof a transverse pin 119. Each of the actuators 116 additionally has acylinder end coupler 120 is pivotally coupled to the respective actuatorbracket 108 by a pin 110, as noted above.

The wheel assembly 113 includes a pair of spaced apart, mirror imagewheel suspensions 122. Each of the wheel suspensions 122 includes asubstantially vertically disposed king pin 124. The wheel suspension 122is free to rotate about the king pin 124. A steering actuator 126 isoperably coupled to each of the respective wheel suspension 122. Thesteering actuator 126 includes a piston end coupler 128 that is coupledto the wheel suspension 122 offset from a stub axle 130 and the king pin124. A cylinder end coupler 132 of the steering actuator 126 ispivotally coupled to a steering bracket 134 mounted proximate the rearmargin of the axle plate 112.

The wheel assembly 113 further includes a rim 136 rotatably mounted tothe stub axle 130 and a preferably pneumatic tire 138 mounted on the rim136.

A pair of spaced apart markers 140 are operably coupled to the uppermargin of the axle plate 112. The markers 140 may be reflectors and/orelectric lights.

The second members of the merger 10 of the pick-up head members 14, 16,and 18. It should be noted that each of the pick-up head members 14, 16,18 is virtually identical, so that the description below applies to allthree. The pick-up head members 14, 16, 18 include two majorsubassemblies, conveyor assembly 146 and pick-up assembly 148.

The conveyor assembly 146 is best viewed in FIGS. 3, 7 and 8. Each ofthe conveyor assemblies 146 includes a frame 150. The frame 150 includesa rear rail 152 and a front rail 154. A plurality of frame members 155extend between the rear rail 152 and the front rail 154.

A forward arching deflector 156 is fixedly coupled to the rear rail 152and partially overlies a conveyor 158.

The conveyor 158 is endless and is supported by a pair of spaced apartrotatable axles 160. The conveyor 158 is formed of a plurality of linkedsegments 161. The upper surface of the conveyor 158 translates asindicated by the arrow 162. Accordingly, crop deposited on the conveyor158 is transferred leftward in the depiction of FIG. 3.

A preferably hydraulic drive system 164 is mounted on the rear face ofthe rear rail 152. The hydraulic drive system 164 is operably coupled tothe conveyor 158 for imparting the travel indicated by the arrow 162 tothe conveyor 158.

The second subassembly of the pick-up head members 14, 16, 18 is thepick-up assembly 148. The pick-up assembly 148 of each of the pick-uphead members 14, 16, 18 includes a generally planar end plate 174. Theend plate 174 preferably includes a recessed mount 176 for an interiorlydisposed drive shaft bearing (not shown). As described below, the driveshaft bearing rotatably supports a drive shaft 196. The planar end plate174 is a highly advantageous feature of the merger 10. By being planarand not obstructed other items (specifically, prior art mergerstypically have a motor for rotationally driving tines disposed on theendplate), adjacent pickup head members are capable of being broughtinto very close proximity. Such closeness facilitates minimalinterruption in the pickup of crop along the full front face to thepick-up head members 14, 16, 18. Additionally, the space betweenadjacent conveyor assemblies 146 is minimized and crop loss that mightoccur during the transfer of crop to an adjacent conveyor assembly 146is minimized.

The pick-up assembly 148 of each of the pick-up head members 14, 16, 18further include a plurality of spaced apart, semi-circular fixed spacers178. A plurality of rotatable tines 180 project through the aperturesdefined between adjacent fixed spacers 178.

The rotatable tines 180 are powered by an internal drive assembly 182 asdepicted in FIGS. 4, 4 a. The internal drive assembly 182 includes adrive mount plate 184 that is fixedly coupled to a housing 186. Thedrive mount plate 184 fixes the internal drive assembly 182 within thegenerally circular aperture defined internal to the fixed spacers 178and the tines 180. It is significant to note that the internal driveassembly 182 is positioned approximately midway between the two endplates 174 of a respective pickup head member 14, 16, 18, as indicatedin FIG. 4. The disposition of the internal drive assembly 182 within theinternal aperture defined by the fixed spacers 178 and the tines 180frees up the end plates 174 so that adjacent pick-up head members 14,16, 18 can be disposed very closely together thereby ensuring a moreefficient pick-up of crop and lateral conveying of the crop once pickedup.

A motor 188 is mounted on the housing 186. The mounting is affected bymating a flange 190 to the housing 186 preferably by means of bolts. Atleast two hydraulic lines 192 provide hydraulic fluid to the motor 188.

The housing 186 provides a mount for a transmission 194. Thetransmission 194 preferably is comprised of two meshed gears, preferablyof the same size. The 1:1 ratio of the gears of the transmission 194preferably matches the revolutional speed of the drive shafts 196, 198to the output shaft of the motor 188.

One of the gears in the transmission 194 is fixedly coupled to the driveshafts 196, 198. The respective drive shafts 196, 198 are operablycoupled to a plurality of tine mounting shafts 199, such that rotationof the respective drive shafts 196, 198 by the motor 188 result inimparting rotational motion to the plurality of tine mounting shafts199.

A cam 200 is fixedly coupled to the housing 186. The cam 200 has achannel 201 defined between an inner cam race 202 and an outer cam race203. A cam follower 204 is fixedly coupled to each of the plurality oftine mounting shafts 199. Each of the cam followers 204 includes aroller 206 coupled proximate an end of the cam follower 204 by means ofa coupler 208. The follower arm 210 of the cam follower 204 is coupledto the tine mounting shaft 199 by means of a welded coupler 212. Thecoupler 212 additionally fixedly couples the tine 216 to the tinemounting shaft 199.

Referring to FIG. 5, it should be noted that the cam 200 has a generallyoval shape, peaking at an apex at the top and at the bottom of the cam200. Accordingly, a lesser arc 220 is presented at the top and bottom ofthe cam 200 and a greater arc 218 is presented by the cam 200 at itsforward face and at its rearward face, forward being defined as to theright in FIG. 5 and rearward as being defined as to the left in FIG. 5.

FIGS. 6-8 depict a pair of skid plates 230 mounted beneath each of thepick-up head members 14, 16, 18. Each of the skid plates 230 includes aground engaging plate 231. The plate 231 is mounted on a shiftable mount232. The shiftable mount 232 includes a pair of actuators 234. Theactuators 234 are coupled at a first end to the plate 231 and at asecond end to the frame 150. Selective porting of hydraulic fluid to theactuators 234 shifts the plate 231 relative to the underside of therespective pick-up head members 14, 16, 18, thereby setting the desiredheight of the respective pick-up head members 14, 16, 18 relative to theunderlying ground.

In operation, the merger 10 is shiftable between a transport disposition(FIG. 7) and a working disposition (FIGS. 1-3). In the transportdisposition, the two pick-up head members 14 and 16 are in an elevateddisposition with the pick-up assemblies 148 thereof defining theuppermost dimension of the merger 10. As noted above, pick-up headmember 18 is fixed and remains essentially in the same disposition thatpick-up head member 18 assumes during working operations. The truckassembly 26 may be rotated relative to the support assembly 24 toelevate the merger 10 above the underlying ground as desired. This isaffected by extending actuators 116, thereby causing the truck assembly26 to rotate above the pin 103 and assume the position more tucked underthe chassis member 12 of the merger 10.

Shifting the merger 10 from the transport disposition to the workingdisposition involves a number of steps. Preferably, such shifting iseffected by moving one pick-up head member 14, 16 at a time in order toconserve on the volume of high pressure hydraulic fluid required tocomplete the operation. Accordingly, in the depiction of FIG. 8, pick-uphead member 16 has been shifted from the essentially verticaldisposition of FIG. 7 to a substantially horizontal disposition. Suchshifting is effected by extending lift actuator 88, thereby causing therespective pick-up head member 14, 16 to rotate about the pin 80. Thisdisposition is depicted for pick-up head member 16 in FIG. 8 and pick-uphead member 14 in FIG. 9.

The next step is to rotate the respective pick-up head member 14, 16through an arc of approximately 90 degrees into alignment with thepick-up head member 18 in the working disposition. Such action iseffected by extending the translation actuator 82, thereby causing therespective pick-up member 14, 16 to rotate about the essentiallyvertically disposed pin 87 of the coupler 85.

Once the three pick-up head members 14, 16, 18 are disposed in theworking disposition depicted in FIGS. 1-3, the height of the merger 10relative to the underlying ground may be adjusted as desired by movingthe shiftable mount 232 of the respective skid plates 230 to set therespective plates 231 a desired distance from the underside of therespective pick-up head members 14, 16, 18. Additionally, the truckassembly 26 may be rotated to a desired position relative to the supportassembly 24 in order to adjust the rear portion of the merger 10relative to the underlying ground.

As the merger 10 is towed across a field, the pick-up head members 14and 16 are subject to rise and fall responsive to undulations in theunderlying ground. Accommodating the rise, the respective pick-up headmembers 14, 16 is beneficial, but it is also important to bring therespective pick-up head members 14, 16 back into contact with the groundas the ground falls away. Accordingly, the merger 10 employed ahydraulic accumulator 97 fluidly coupled to a respective lift actuator88. As the respective pick-up head member 14, 16 rises, the piston ofthe respective lift actuator 88 is forced back into its cylinder. Suchaction increases the pressure of the hydraulic fluid in the liftactuator 88. This rise in pressure can be transferred to the hydraulicaccumulator 97 and is available there to be transferred back to the liftactuator 88 as the respective pick-up head member 14, 16 drops backdown. As such, the recovered hydraulic pressure of the lift actuator 88acts to force the respective pick-up head member 14, 16 downward afterhaving passed over a rise in the underlying ground. Should such actionnot be desired, the valve 98 is available in order to isolate theaccumulator 97 from the lift actuator 88.

Pick-up of the crop in a field is affected by the rotating tines 216 andthe crop is merged by conveyance on the respective conveyors 158. Thetines 216 are typically rotated in the direction as indicated by arrow222 of FIG. 1. Accordingly, the tines 216 pick-up crop and translatedupward across the weeded face of the respective pick-up assembly 148. Asthe roller 206 coupled to a respective tine 216 approaches the apex ofthe cam 200, effective rotational speed of the tine 216 is acceleratedthereby imparting a flicking motion to the crop being conveyed by thetine 216. Such motion causes the crop to be spread rather more evenlyacross the full width of the conveyor 158. The crop is then conveyed tothe outboard end of the pick-up head member 14 and deposited in awindrow on the ground.

The embodiments above are intended to be illustrative and not limiting.Additional embodiments are within the claims. In addition, although thepresent invention has been described with reference to particularembodiments, those skilled in the art will recognize that changes can bemade in form and detail without departing from the spirit and scope ofthe invention. Any incorporation by reference of documents above islimited such that no subject matter is incorporated that is contrary tothe explicit disclosure herein.

What is claimed is:
 1. A windrow merger employing at least one conveyorfor transporting material picked up by at least one pickup head member,comprising: the at least one pickup head member having a plurality ofspaced apart spacers disposed along a length dimension of the at leastone pickup head member, and an internal drive assembly disposed within alongitudinal aperture defined internal to the plurality of spaced apartspacers, the drive assembly for imparting a rotational motion to aplurality of tines.
 2. The windrow merger of claim 1, the internal driveassembly being disposed generally midway along the length dimension ofthe at least one pickup head member.
 3. The windrow merger of claim 2,the internal drive assembly being operably, rotationally coupled to atleast a first drive shaft for rotation thereof, the rotation of the atleast a first shaft imparting rotational motion to the plurality oftines.
 4. The windrow merger of claim 3, the internal drive assemblyincluding a motor, the motor being operably coupled to the at least afirst shaft by means of a transmission.
 5. The windrow merger of claim4, the transmission including a first gear in a meshed relationship witha second gear.
 6. The windrow merger of claim 5, the transmission firstand second gears having a 1:1 relationship.
 7. The windrow merger ofclaim 4, the motor and the first and second drive shafts being matchedin rotational speed.
 8. The windrow merger of claim 1, the at least onepickup head member having a first and a second generally planar spacedapart end plates.
 9. A method of forming a windrow merger, includingproviding at least one conveyor for transporting material picked up byat least one pickup head member, providing the at least one pickup headmember with a plurality of spaced apart spacers disposed along a lengthdimension of the at least one pickup head member, and disposing aninternal drive assembly within a longitudinal aperture defined internalto the plurality of spaced apart spacers, the drive assembly imparting arotational motion to a plurality of tines.
 10. A windrow merger having amaterial conveyor and an internal drive assembly, the drive assemblybeing disposed generally in an internal aperture defined internal to aplurality of rotatable tines.
 11. The windrow merger of claim 10, theinternal drive assembly including a motor, the motor being coupled to atransmission.
 12. The windrow merger of claim 10, the internal driveassembly being operably coupled to at least one drive shaft, the atleast one drive shaft being operably coupled to a plurality of tines forimparting a rotational motion to the tines.
 13. The windrow merger ofclaim 10, the disposition of the internal drive assembly acting to freeopposed end plates of a pickup assembly of obstructions coupled thereto.14. The windrow merger of claim 10, further including a rotationimparted to the plurality of tines being a cammed rotation, the cammingof the rotation effecting a varying rotational speed of the tines. 15.The windrow merger of claim 14, the rotational speed of the tines beingaccelerated just prior to discharge of a crop being borne by the tines.16. The windrow merger of claim 15, further including at least one cam,the cam having an apex, the apex acting on passing tines to effect anacceleration of the rotational speed of the tines.
 17. The windrowmerger of claim 16, the at least one cam having a generally oval shape.18. The windrow merger of claim 17, the at least one cam being coupledto an internal drive assembly.
 19. A method of forming a windrow mergerincluding forming an internal drive assembly and disposing the driveassembly generally in an internal aperture defined internal to aplurality of rotatable tines.
 20. A method of forming a windrow mergerincluding forming a plurality of rotationally drivable tines, impartinga cammed rotation to the tines, the camming of the rotation effecting avarying rotational speed of the tines.